US4775042A - Clutch disc - Google Patents

Clutch disc Download PDF

Info

Publication number
US4775042A
US4775042A US06/836,507 US83650786A US4775042A US 4775042 A US4775042 A US 4775042A US 83650786 A US83650786 A US 83650786A US 4775042 A US4775042 A US 4775042A
Authority
US
United States
Prior art keywords
clutch disc
drive
driven
fluid
side arm
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/836,507
Other languages
English (en)
Inventor
Satoshi Kohno
Kazuhiro Kikuchi
Youichiro Yamada
Tsutomu Nomura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Atsugi Motor Parts Co Ltd
Original Assignee
Nissan Motor Co Ltd
Atsugi Motor Parts Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP60044112A external-priority patent/JPH0646052B2/ja
Priority claimed from JP4411185A external-priority patent/JPS61201931A/ja
Priority claimed from JP1985093287U external-priority patent/JPH038810Y2/ja
Priority claimed from JP12015685U external-priority patent/JPH0247770Y2/ja
Application filed by Nissan Motor Co Ltd, Atsugi Motor Parts Co Ltd filed Critical Nissan Motor Co Ltd
Assigned to NISSAN MOTOR CO., LTD., ATSUGI MOTOR PARTS CO., LTD. reassignment NISSAN MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KIKUCHI, KAZUHIRO, KOHNO, SATOSHI, NOMURA, TSUTOMU, YAMADA, YOUICHIRO
Application granted granted Critical
Publication of US4775042A publication Critical patent/US4775042A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/161—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material characterised by the fluid damping devices, e.g. passages, orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/80—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/165—Sealing arrangements

Definitions

  • the present invention relates generally to a driven clutch disc forming part of a clutch used in automotive vehicles and the like, and more particularly to the clutch disc of the type wherein a hydraulic fluid is used to constitute a damper for suppressing vibration applied to the clutch disc.
  • This clutch disc includes the damper disposed between drive (input) and driven (output) bodies which are connected to be rotatable relative to each other.
  • the damper consists of an elastic cylindrical member provided at the opposite ends with damper sheets which are engaged with the drive body.
  • a relatively thin partition plate fixed to the driven body is provided to divide the inside of the elastic cylindrical member into two chambers which are filled with the hydraulic fluid. Additionally, the partition plate is formed with an orifice through which the two chambers are in fluid communication with each other for the purpose of providing flow resistance to fluid flow between the two chambers.
  • the thus arranged conventional clutch disc operates as follows: When a relative rotation is made between the drive and driven bodies to abruptly compress one of the two chambers, an abrupt pressure rise is produced in the compressed chamber and then gradually released through the orifice into the other chamber, thereby effectively damping torque fluctuation of a drive system.
  • drawbacks have been encountered in the conventional clutch disc in which a sufficient damping effect has not been exhibited thereby making it impossible to obtain a greater damping amount, for the reason that the length of the orifice is smaller because the orifice is formed through the relatively thin partition plate.
  • a clutch disc consists of a generally annular driven body including a radially outwardly extending flange section.
  • the flange section has a plurality of driven side arms which radially outwardly extend and are located at equal intervals in the direction of periphery of the driven body.
  • a generally annular drive body is movably connected with the driven body in such a manner as to drive the driven body to allow a relative rotation therebetween.
  • the drive body includes a cover section disposed to cover the driven body flange section, and a plurality of drive side arms which radially inwardly extend and are located at equal intervals in the direction of periphery of the drive body.
  • a fluid chamber is defined between one of the driven side arms and one of the drive side arms and filled with a fluid, in which the adjacent two fluid chambers constitute a damping unit. Additionally, an orifice is formed to establish communication between the adjacent two fluid chambers constituting the damping unit. The orifice is formed under cooperation of at least one of each driven side arm and each drive side arm.
  • the orifice is located far from the rotational axis of the drive and driven bodies, and additionally is formed longer in the peripheral direction of the clutch disc, thereby providing a larger damping force. This effectively prevent generation of booming noise due to torsional resonance vibration and vibration during vehicle acceleration and deceleration.
  • the orifice is formed in at least one of each driven side arm and each drive side arm which has a relatively large thickness in the peripheral direction, the length of the orifice becomes larger and therefore the orifice can be provided with a mechanism for controlling the cross-sectional area of the orifice in accordance with the angle of relative rotation between the drive and driven bodies, thereby providing an appropriate damping force in accordance with the magnitude of torque fluctuation applied from an engine side to this clutch disc.
  • FIG. 1 is a front view, being partly cut away, of a first embodiment of a clutch disc according to the present invention
  • FIG. 2 is a cross-sectional view taken in the direction of arrows substantially along the line 2--2 of FIG. 1;
  • FIG. 3 is a schematic illustration showing the state of the clutch disc of the FIG. 1 in which a drive body rotates in the peripheral direction;
  • FIG. 4 is a front view similar to FIG. 1 but showing a second embodiment of the clutch disc according to the present invention
  • FIG. 5 is a fragmentary sectional view taken in the direction of arrows substantially along the line 5--5 of FIG. 4;
  • FIG. 6 is a front view similar to FIG. 1 but showing a third embodiment of clutch disc according to the present invention.
  • FIG. 7 is a cross-sectional view taken in the direction of arrows substantially along the line 7--7 of FIG. 6;
  • FIG. 8 is front view similar to FIG. 1 but showing a fourth embodiment of the clutch disc according to the present invention.
  • FIG. 9 is a cross-sectional view taken in the direction of arrows substantially along the line 9--9 of FIG. 8;
  • FIG. 10 is a cross-sectional view similar to FIG. 9 but showing a fifth embodiment of the clutch disc according to the present invention.
  • FIG. 11 is a cross-sectional view similar to FIG. 9 but showing a sixth embodiment of the clutch disc according to the present invention.
  • FIG. 12 is a cross-sectional view similar to FIG. 9 but showing a seventh embodiment of the clutch disc according to the present invention.
  • FIG. 13 is a fragmentary enlarged sectional view of an essential part of an eighth embodiment of the clutch disc according to the present invention.
  • FIG. 14 is a fragmentary enlarged sectional view of an essential part of a ninth embodiment of the clutch disc according to the present invention.
  • FIG. 15 is a fragmentary enlarged sectional view of an essential part of a tenth embodiment of the clutch disc according to the present invention.
  • FIG. 16 is a cross-sectional view similar to FIG. 9 but showing an eleventh embodiment of the clutch disc according to the present invention.
  • FIG. 17 is an enlarged sectional view of an essential part of FIG. 16;
  • FIG. 18 is a front view similar to FIG. 1 but showing an twelfth embodiment of the clutch disc according to the present invention
  • FIG. 19 is a cross-sectional view taken in the direction of arrows substantially along the line 19--19 of FIG. 18;
  • FIG. 20 is an enlarged sectional view of an essential part of the clutch disc of FIG. 18, illustrating a state where a floating member is in a neutral position;
  • FIG. 21 is an enlarged sectional view similar to FIG. 20 but illustrating another state where the floating member has been moved leftward from the neutral position;
  • FIG. 22 is an enlarged sectional view similar to FIG. 20 but showing a thirteenth embodiment of the clutch disc according to the present invention, illustrating a state where a floating member is in a neutral position;
  • FIG. 23 is an enlarged sectional view similar to FIG. 22 but illustrating another state where the floating member has been moved leftward from the neutral position;
  • FIG. 24 is a cross-sectional view similar to FIG. 1 but showing a fourteenth embodiment of clutch disc according to the present invention.
  • FIG. 25 is a cross sectional view taken in the direction of arrows substantially along the line 25--25 of FIG. 24.
  • FIGS. 1 and 2 there is shown a first embodiment of a driven clutch disc in accordance with the present invention.
  • the clutch disc forming part of a clutch which is arranged to connect an engine and adrive line to power a vehicle and to disconnect the engine and the drive line.
  • the clutch disc comprising a driven or power output body 3 which is generally annular and formed at its inner periphery which a splined portion 1 with which a power output shaft of the drive line is engaged.
  • the driven body 3 includes a flange section 2 which extends radially and outeardly.
  • the flange section 2 is formed with a plurality (three) of driven side arms 6 which extend radially outwardly and are located at equal intervals in the direction of periphery of the flange section 2.
  • a drive or power input body 5 includes a cover section 4 disposed along the driven body flange section 2 in such a manner as to cover the flange section 2.
  • the drive body 5 is rotatably movable relative to the driven body 3 and formed with a plurality (three) of drive side arms 7 which project radially inwardly at equal intervals in the direction of peripheryof the drive body 5.
  • a fluid chamber 8 is defined between the adjacent drive and driven side arms 6, 7, so that a plurality of fluid chambers 8 are provided in the clutch disc.
  • an elastic body 9 is disposed within a fluid chamber 8 so that a plurality (six) of elastic bodies 9 are provided in whole the clutch disc.
  • a hydraulic or operating fluid such as silicone oil is filled in all the fluid chambers 8.
  • an orifice 10 is formed between the inner periphery of the drive body 5 and the radially outer-most portion of each driven side arm 7so that a plurality of the orifices 10 are provided in whole the clutch disc.
  • Each orifice 10 functions to provide a flow resistance to flow movement of the fluid to be made between the adjacent fluid chambers 8, thereby damping the torsional vibration generated between the drive and driven side bodies 5, 3.
  • the drive body 5 includes a pair of generally annular drive plates 5a, 5b which are located opposite to each other and disposed on the opposite sides of the flange section 2, thereby forming the cover section 4.
  • the drive plates 5a, 5b are connected together at their outer peripheral portion and together with a cushioning plate 11 by means of cushioning rivets 12.
  • a generally annular backing plate 5c is disposed inside cover section 4 and connected to cover section 4 in such a manner as to prevent the backing plate 5c from its rotational movement in the peripheral direction by means of a plurality of rounded projections which are in engagement with inner peripheral surface of the cover section 4 or the connected opposite drive plates 5a, 5b.
  • the backing plate 5c includes an annular section 5d disposed along the inner peripheral surface of the cover section 4 so as to be in direct contact with the drive plates 5a, 5b.
  • the three drive side arms 6 are projected radially inwardly from the annular section 5d.
  • Each drive side arm 6 is generally in the triangular shape in cross-section in an imaginary plane perpendicular to the axis of the backing plate 5c, in which the width of the arm becomes smaller in the radially inward direction; however, the most-outward portion of the arm is slightly widended as shown in FIG. 1.
  • each of the three driven side arms 7 located between the drive side arms 6 along the peripheral direction of the backing plate 5c.
  • Each driven side arm 7 is generally in the triangular shape in the cross-section in the imaginary plane, in whichthe width of the arm becomes larger in the radially outward direction.
  • Eachdriven side arm 7 has at its outer-most portion two opposite corners C 1 , C 2 extending in the axial direction of the drive body 3.
  • Thedriven side arm 7 is formed between the corners C 1 , C 2 with the outer-most surface 7c having a same curvature as that of the inner periphery of the backing plate 5c. It will be understood that a small clearance serving as the orifice 10 is formed between the outer-most surface of the driven side arm 7 and the inner peripheral surface of the backing plate 5c.
  • Beveling is made to the axially extending corners C 1 , C 2 of the driven side arm 7 so that the fluid within the fluid chamber 8 is smoothly introduced into the orifice 10 thereby to obtain stable damping ability.
  • the opposite side facesF 1 , F 2 of the driven side arm 7 is in slidable contact with the inner surfaces of the drive plates 5a, 5b.
  • the opposite side faces (not identified) of the drive side arm 6 are in slidable contact with the inner surfaces of the drive plates 5a, 5b.
  • Each elastic body 9 is disposed between the adjacent drive and driven side arms 6, 7 and consists of large-diameter and small-diameter compression springs 9a, 9b which are coaxially disposed in such a manner as to providea biasing force to the drive and driven side arms 6, 7 in the direction to separate the arms 6, 7 from each other.
  • the opposite ends of each spring 9a, 9b are in press contact with the spring retainer faces 6a, 7a of the drive and driven arms 6, 7, respectively.
  • the free length of the springs 9a, 9b is longer than the total of a peripheral direction distance Q 1 of the fluid chamber 8 in a standard condition before operation of the clutch disc and an extended peripheral direction distance Q 2 of the fluid chamber 8 in a condition where the maximum torsional angle is made in the clutch disc, thereby preventing each spring 9a, 9b from chattering during operation of the clutch disc.
  • a seal ring 13 is disposed between the peripheral portions of the drive plates 5a, 5b to prevent the fluid inthe fluid chambers 8 from leaking out of the fluid chambers 8.
  • Annular sealmembers 14 serving also as bearings are disposed between the hub 3a of the driven body 3 and the drive plates 5a, 5b for the purpose of preventing leaking of fluid to the outside of the fluid chamber 8.
  • An air chamber 19 is formed between the driven body 3 and each seal member 14.
  • the drive plate 5a is formed with a hole 16 through which the fluid is poured into and discharged from the fluid chamber 8.
  • the hole 16 is closed by a threaded plug 15.
  • annular clutch or friction facings 17 are secured to cushioning plate 11 by means of facing rivets 18.
  • the orifice 10 for damping torsional vibration generated in a drive system is formed between the outer-most surface f the driven side arm 7 and the inner periphery of the drive body 5, the orifice 10 is located far from the rotational axis O of the drive and driven side bodies 5, 3, thereby obtaining a greater dampingeffect. Furthermore, by virtue of the fact that the orifice 10 is defined by the considerably long outer-most surface of the driven side arm 7 whosewide becomes larger in the radially outward direction, the peripheral length of the orifice 10 is formed longer, thereby providing a greater flow resistance to the fluid flow between the adjacent fluid chambers 8, thus to obtain a greater amount of damping.
  • the variation in damping amount can be suppressed to a lower level since the silicone oil has a relatively high heat resistance temperature and is less in viscosityvariation. This provides a stable damping characteristics throughout a widerange of temperatures at which the clutch disc is used.
  • each elastic body 9 is set longer than the total of the peripheral direction distance Q 1 in the standard condition before operation of the clutch disc and the extended peripheral direction distance Q 2 in the condition of the maximum torsional angle of the clutch disc, the opposite ends of each elastic body 9 can be kept in elastic contact with the spring retainer faces 6a, 7a, respectively, even in the case where theclutch disc becomes into the clutch disc maximum torsional angle condition.Consequently, even when each elastic body 9 receives a centrifugal force generated by the operation of the clutch disc, the location of each elastic body 9 cannot shift radially and outwardly, thus always maintaining the elastic body 9 in a proper location posture. Besides, thisprevents generation of noise caused by the play in the clutch disc during operation, while avoiding abnormal wear made between each elastic body 9 and the drive and driven bodies 5, 3.
  • FIGS. 4 and 5 illustrates a second embodiment of the clutch disc according to the present invention, which is similar to the first embodiment except for the installation structure of the drive side arms 6.
  • the drive side arms 6 are disposed inside the cover section 4 formed of the drive plates 5a, 5b and located at equal intervals in the peripheral direction of the cover section 4. The thus disposed each drive side arm 6 is secured in position by means of a plurality of fixing pins 20 as shown in FIG. 5.
  • the annular section 5d of the backing plate 5c is omitted and therefore not only material cost can be reduced, but also the radius l of the driven side arm 7 is enlarged by an amount corresponding to the thickness (or the radial direction width) of the annular section 5dof the backing plate 5c.
  • the locus of the radius l corresponds to the above-mentioned curvature of the outer-most surface of the drive side arm 7. This makes the location of the orifice 10 farther from the rotational axis O of the drive and driven bodies 5, 3 thereby further enlarging the peripheral length of the orifice 10. This provides a further greater damping amount in the clutch disc.
  • FIGS. 6 and 7 illustrate a third embodiment of the clutch disc according tothe present invention, which is similar to the first embodiment with the exception that each of the drive and driven side arms 6, 7 is provided with a volume change compasating section 13 for compasating the volume change of the hydraulic fluid filled in the fluid chambers 8 which volume change is due to temperature change of the fluid.
  • the volume change compensating section 13 includes a hollow elastic (elastomeric) member 13adisposed within a cylindrical through-hole 6c formed in each of the drive and driven side arms 6, 7.
  • the through-hole 6c has an axis extending parallel with the rotational axis O of the drive and driven bodies 5, 3. In other words, the through-hole 6c extends in the direction of thickness of each of the drive and driven side arms 6, 7.
  • a gas such as air is confined inside the hollow elastic member 13a.
  • the fluctuation of thedriving torque is absorbed under the spring reaction of the elastic members9, and the rotational direction vibration of the drive body 5 to the drivenbody 3 is damped in the same manner as in the first and second embodiments.
  • the elastic member 13a contracts thereby to absorb the thermally expanded amount of the fluid. Accordingly, the fluid within the fluid chamber 8 is prevented from containing gas bubble, thus avoiding the fact that damping characteristics becomes unstable due to thecompression of the gas bubble.
  • the elastic member 13a expands by the amount corresponding to the contracted amount of the fluid to fill the fluid chambers 8 with the fluid, thereby preventing air from entering the fluid chambers 8.
  • FIGS. 8 and 9 illustrate a fourth embodiment of the clutch disc according to the present invention, which is similar to the third embodiment with the exception that the volume change compensating section 13 is replaced with that 13A.
  • the volume change compensating section 13A in this embodiment includes annular elastic (elastomeric) tubes 13b, 13c inside which a gas is confined.
  • the elastic tubes 13b, 13c are respectively disposed in annular grooves 2a, 2b formed in the flange section 2 of the driven body 3 in such a manner as to surround the hub section 3a of the driven body 3.
  • the annular grooves 2a, 2b are formed on the opposite side faces F 3 , F 4 of the driven body flange section 2 which side faces are is in slidable contact with the inner surfaces of the drive plates 5a, 5b, respectively.
  • the fourth embodiment clutch disc when the fluid filled in the fluid chambers 8 makes its volume change due to temperature change, the volume change is compensated by the elastic expansion or contraction of the elastic tubes 13b, 13c. Additionally, since the elastictubes 13b, 13c are located along the peripherally arranged fluid chambers 8, a part of the fluid flowing out of each fluid chamber 8 through the clearances C 1 , C 2 can be uniformly received by the elastic tubes13b, 13c, thereby absorbing the volume change of the fluid in the fluid chambers 8 throughout whole the elastic tubes 13b, 13c. Besides, the installation operation of the elastic tubes 13b, 13c is completed merely by placing the elastic tubes 13b, 13c into the annular grooves 2a, 2b of the driven body flange section 2, thus facilitating the assembly operationof the clutch disc.
  • FIG. 10 illustrates a fifth embodiment of the clutch disc according to the present invention, which is similar to the third embodiment with the exception that the volume change compensating section 13 is replaced with that 13B.
  • the volume change compensating section 13B of this embodiment includes an elastic (elastomeric) diaphragm 13d which is spreaded to coverthe opening of a cylindrical hole 7b maintaining a fluid-tight seal.
  • the periphery of the elastic diaphram 13e is fixed through an annular retainer13d to a portion of each driven side arm 7 which portion surrounds the opening of the cylindrical hole 7b.
  • the cylindrical hole 7b is formed in each driven side arm 7 and so located that axis thereof is parallel with the rotational axis 0 of the drive and driven bodies 5, 3.
  • the opening of the cylindrical hole 7b is formed at one side face F 2 of each driven side arm 7, in which the elastic diaphram 13e is located slightly spaced from and opposite to the inner surface of the drive plate 5b.
  • the inside of the cylindrical hole 7b is filled with a gas.
  • the elasticdiaphram 13e expands and contracts due to temperature change of the fluid within the fluid chambers 8, thus compensating the volume change of the fluid.
  • FIG. 11 illustrates a sixth embodiment of the clutch disc in accordance with the present invention, which is provided with the volume change compensating section 13C similar to that of the fifth embodiment.
  • the volume change compensating section 13C includes another elastic (elastomeric) diaphram 13e' in addition to the elastic diaphram 13e.
  • the elastic diaphram 13e' is spreaded to cover an opening of a through-hole 13f formed in each driven side arm 7 in such a manner that the axis thereof is parallel with the rotational axis O of the drive and driven side bodies 5, 3.
  • the through-hole opening covered with the elasticdiaphram 13e' is formed at the side face F 1 of each driven side arm 7,in which the periphery of the elastic diaphram 13e' is fixed through a retainer 13d' to a portion of the drive side arm 7 surrounding the through-hole opening.
  • the elastic diaphram 13e' is located slightly spacedfrom and opposite to the inner surface of the drive plate 5a.
  • the elastic diaphram 13e is disposed to cover the other opposite opening of the through-hole 13f in the same manner as in the fifth embodiment.
  • both the elastic diaphram 13d, 13d' can make their elastic expansion and contraction with temperature change of the fluid within the fluid chambers 8, thereby compensating for the volume change of the fluid flowing through the clearances C 1 , C 2 between the fluid chambers 8.
  • FIG. 12 illustrates a seventh embodiment of the clutch disc in accordance with the present invention.
  • the flange section 2 of the driven body 3 is formed with two annular grooves 2d, 2d which are located in the vicinity of the hub or boss section 3a in such a manner as to surround the hub section 3a.
  • One of the annular grooves 2d, 2d opens tothe side face F 3 of the flange section 2 while the other opens to the side face F 4 of the same.
  • the drive plates 5a, 5b are inwardly bent at their central portion defining a center opening (no numeral) in which the driven body hub section 3a is located, thereby forming cylindrical bent sections 5e, 5e which are opposite to each other.
  • annular chamber 13g is defined between the cylindrical inner wall surface of the bend section 5e and the outer cylindrical wall surface of the annular groove 2 d.
  • the cylindrical inner wall surface of the bend section 5e and the outer cylindrical wall surfaceof the annular groove 2d are coaxial with each other and extend parallel with the rotational axis O of the drive and driven bodies 5, 3.
  • Two annular seal members 13h, 13h forming part of the volume change compensating section 13D are fittingly disposed within the annular chambers 13g, 13g, respectively, and are slidable in the axial direction of the clutch disc.
  • a elastic or spring member 13i is disposed between each annular seal member 13h and the bottom surface of each annular groove2d in such a manner as to provide a biasing force to each seal member 13h in the direction to always urge each seal member 13h outwardly, in which the seal member 13h is allowed to slidingly move inwardly and outwardly inaccordance with volume change of the fluid filled in the fluid chambers 8 which volume change is due to temperature change.
  • a bearing 20 is disposedbetween each drive plate bent section 5e and the inner cylindrical wall surface of the annular groove 2d or the outer surface of the hub section 3a to make further smooth the relative rotation between the drive and drive bodies 5, 3.
  • FIG. 13 illustrates an eighth embodiment of the clutch disc in accordance with the present invention, which is similar to the fifth embodiment of FIG. 10 with the exception that the elastic diaphram 13e is replaced with a movable wall member 13k provided with a seal member 13j.
  • the movable wall member 13k is fittingly disposed within the cylindrical hole 7b.
  • the movable wall member 13k is always biased outwardly by means of an elastic or spring member 13l, so that the movable wall member 13k is movable inwardly and outwardly in accordance wih the volume change of the fluid within the fluid chambers 8. It will be understood that the volume change of the fluid with temperature change can be compensated by the axial movement of the movable wall member 13k.
  • FIG. 14 illustrates a ninth embodiment of the clutch disc in accordance with the present invention, which is similar to the sixth embodiment of FIG. 11 with the exception that the elastic diaphrams 13e, 13e' are respectively replaced with the movable wall member 13k and another movablewall member 13k'.
  • the two movable wall members 13k, 13k' are fittingly and slidably disosed in the through hole 13f and located in parallel with eachother.
  • the elattic or spring member 13l is disposed between the movable wall members 13k, 13k' to bias them in the direction to separate from eachother.
  • the movable wall member 13k, 13k' are axially movable in accordance with the volume change of the fluid within the fluid chambers 8, thereby compensating for the volume change of the fluid due to temperature change.
  • FIG. 15 illustrates a tenth embodiment of the clutch disc in accordance with the present invention, which is similar to the ninth embodiment of FIG. 14 with the exception that the movable wall members 13k, 13k' and theelastic member 13l forming part of the volume change compensating section 13G are disposed in a through-hole 13m formed in each of the drive side arms 6 or in each of the driven side arms 7. As shown, the through-hole 13m is formed in such a manner that the adjacent fluid chambers 8, 8 are communicated with each other therethrough.
  • each spring retainer 13n appears to prevent the communication between the through-hole 13m and the fluid chamber 8, fluid communication is made through a small clearancebetween the spring retainer 13n and the spring retaining face 6a (7a) of the drive or driven side arm 6 (7).
  • the spring retainer 13h is used for the purpose of stably retaining the elastic member 9. It is preferable that a groove (not shown) having a cross-sectional area smaller than the orifice 10 is formed on the spring retaining face 6a (7a) or on the face of the spring retainer 13h facing to the spring retaining face 6a (7a), thereby establishing communication between the inside of the through-hole 13m and the fluid chambers 8.
  • the volume change of the fluid within the fluid chambers 8 can be compensated under the axial movement of the movable wall membes 13k, 13k'.
  • volume change compensating section 13A, 13B, 13C, 13D, 13E, 13F or 13G has been shown and described as being formed in one of the drive and driven bodies 5, 3 in the fourth to tenth embodiments, it will be understood that the volume change compensating section may be formed both in the drive and driven bodies 5, 3, in which a further effective volume change compensation can be accomplished.
  • FIGS. 16 and 17 illustrate an eleventh embodiment of the clutch disc according to the present invention, which is somewhat similar to the seventh embodiment of FIG. 12.
  • the volume change compensating section 13H includes an annular hollow casing 13p whose inside is communicated with the the clearance C 2 between the side face F 2 of the driven side arm 7 and the inner surface of the cover section 4 or of the drive plate 5b, so that the inside of the hollow casing 13p is filled with the fluid.
  • Disposed inside the hollow casing 13p is an annular elastic (elastomeric) tube 13q in which a gas is confined.
  • the reference numeral 21 denotes a seal member for maintaining a fluid-tight seal of the fluid chambers 8.
  • FIGS. 18, 19 and 20 illustrate a twelfth embodiment of the clutch disc in accordance with the present invention, which is similar to the first embodiment with the exception that an orifice for providing a flow resistance to the fluid moving between the adjacent fluid chambers 8 is formed in each drive side arm 6.
  • the flange section 2 of the driven body 3 and the central section of the drive plates 5a, 5b are formed similar to those of the seventh embodiment of FIG. 12, in which the seal members 21, 21 are disposed between the flange section 2 and the drive plates 5a, 5b to maintain a fluid-tight seal therebetween.
  • Each drive side arm 6 of the drive body 5 is formed with a communicating hole 30 through which the adjacent fluid chambers 8, 8 are communicated with each other.
  • the communicating hole 30 includes a first small diametersection 30a merged in one of the adjacent fluid chambers 8.
  • the first smalldiameter section 30a is connected through a large diameter section 30c witha second small diameter section 30b.
  • the large diameter section 30c has a first end in which the first small diameter section 30a merges, and a second end in which the second small diameter section 30b merges.
  • the second small diameter section 30b is formed through a closure plate 31 for closing one end of a large diameter hole (no numeral) a part of which serves as the large diameter section 30c.
  • the first and second small diameter sections 30a, 30b has the same diameter l 1 .
  • the large diameter section 30c has a diameter l 2 larger than the diameter l 1 , defining thereinside a space 32.
  • a floating member 33 is disposed in the space 32 to be axially movable in accordance with the flowing movement of the fluid within the communicatinghole 30.
  • the floating member 33 is formed annular and has cylindrical innerand outer peripheral surfaces which are coaxial with each other.
  • the outer diameter l 3 of the floating member 33 is larger than the diameter l 1 of the first and second small diameter sections 30a, 30b, and smaller than the diameter l 2 of the large diameter section 30c.
  • the floating member 33 is formed at its central section with an orifice or through-hole 33a.
  • annular orifice 33b can be formed between the outer peripheral surface of the floating member 33 and the wall surface of the communicating hole large diameter section 30c. It is to be noted that the total of the cross-sectional areas of the orifices 33a, 33b is larger than the cross-sectional area of each communicating hole small diameter section 30a (30b).
  • the adjacent fluid chambers 8, 8 are balanced in pressure so that no pressure differential isproduced.
  • the floating member 33 is kept to stop in a neutral position within the space 32 as shown in FIG. 20.
  • the drive body 3 rotates in the peripheral direction relative to the driven body 5 so that the drive side arms 6 formed with the backing plate 5c rotates in the same direction. Consequently, the elastic body 9 disposed in one of the adjacent fluid chambers 8, 8 located on the opposite sides of the drive side arm 6 is compressed by the drive side arm 6.
  • the drive torque from the drive system is transmitted through the compressed elastic body 9 to the driven body 3.
  • the floating member 33 slightly moves slidingly but does deach the small diameter section 30a because of the fact that the total cross-sectional area of the orifices 33a, 33b is larger than the cross-sectional area of each small diameter section 30a (30b).
  • the fluid flows from one of the fluid chambers 8, 8 into the other fluid chamber 8 with a predetermined flow resistance due to the flow restriction action of the communicating hole small diameter sections 30a, 30b, thus making a smaller energy loss of the fluid.
  • This provides a smaller damping force, thereby previously preventing generation of boomingnoise due to smaller torque fluctuation.
  • this embodiment can securely provide a variety of appropriate damping forces in accordance with the magnitude of the torque fluctuation transmitted from the drive system.
  • FIGS. 22 and 23 illustrate a thirteenth embodiment of the clutch disc in accordance with the present invention, which is similar to the twelfth embodiment with the exception that the annular floating member 33 is replaced with a spherical floating body 33A.
  • the spherical floating body 33A is movably disposed with the space 32 and has a diameter l 3 ' which is smaller than the diameter l 2 of the large diameter section 30a and larger than the diameter l 1 of the first or second small diameter section 30a, 30b.
  • each of the first and second small diameter sections 30a, 30b is formed non-circular for the purpose of preventing the small diameter sections 30a, 30b from being completely closed with the spherical floating member 33A.
  • each of the first and second small diameter sections 30a, 30b is formed at their cylindrical surface with an axially extending groove 34.
  • the angle of relative movement between the drive and driven bodies 5, 3 is smaller so that the pressure differential between the adjacent fluid chambers 8, 8 is smaller.
  • the spherical floating member 33A slightly moves toward the first small diameter section 30a in the space 32 but does not reach the small diametersection 30a as shown in FIG. 22, forming an orifice 13b' between the outer spherical surface of the floating member 33A and the inner surface of the communicating hole large diameter section 30c.
  • the fluid flowing from one of the adjacent fluid chambers 8, 8 to the other fluid chamber 8 passes through the larger orifice 13b', so that the first and second small diameter sections 30a, 30b are in the fully open state. This produces a smaller energy loss of the flowing fluid, thereby providing a smaller damping force.
  • the communicating hole 30 in which the floating member 33, 33A is disposed has been shown and described as being formed in each drive side arm 6 of the drive body 5 in the twelfth and thirteenth embodiments, it will be understood that the communication hole 30 may be formed in each driven side arm 7 of the driven body 3 or in both the drive and driven side arms 6, 7. It will be appreciated that the floating member 33, 33A can function against the communicating hole second small diameter section 30b in the same manner as against the first small diameter section 34, andtherefore can function same for rotation of the clutch disc in the oppositedirections.
  • the orifices having different cross-sectional areas can be selectively used for the purpose of providing flow resistances to the fluid flowing from one fluid chamber to the other fluid chamber in accordance with the magnitude of thetorque fluctuation transmitted from the drive system of the engine, i.e., the magnitude of the relative rotation angle between the drive or drive bodies. This can provide an appropriate damping force in accordance with the magnitude of the torque fluctuation from the engine drive system.
  • FIGS. 24 and 25 illustrate a fourteenth embodiment of the clutch disc in accordance with the present invention, which is similar to the first embodiment with the exception that an elastic member 40 is disposed in each fluid chamber 8.
  • the drive plates 5a, 5b are formed similar to those of the seventh embodiment of FIG. 12, in which theseal members 21, 21 are disposed between the flange section 2 and the driveplates 5a, 5b to maintain a fluid-tight seal therebetween.
  • the elastic member 40 is generally egg-shaped and fittingly disposed in a groove 6c formed at each of the spring retaining faces 6a, 6a of each drive side arm 6 of the drive body 6. A gas such as air is confined under pressure in the elastic member 40. Accordingly, each elastic member 40 serves also as means for locating the elastic body 9.
  • each elastic member 40 contracts to decrease its volume, thus suppressing pressure fluctuation within each fluid chamber 8.
  • the amount of the fluid passing through the orifice 10 formed between the drive body inner periphery and driven side body arm radially outer-most portion becomes very small or zero, thereby generating a smaller damping force. This minimizes the dynamic spring constant to improve vibration interrupting ability, thereby damping small amplitude torque fluctuation.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
US06/836,507 1985-03-06 1986-03-05 Clutch disc Expired - Fee Related US4775042A (en)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP60-44112 1985-03-06
JP60044112A JPH0646052B2 (ja) 1985-03-06 1985-03-06 クラツチデイスク
JP4411185A JPS61201931A (ja) 1985-03-06 1985-03-06 クラツチデイスク
JP60-44111 1985-03-06
JP1985093287U JPH038810Y2 (enrdf_load_stackoverflow) 1985-06-20 1985-06-20
JP60-93287[U]JPX 1985-06-20
JP12015685U JPH0247770Y2 (enrdf_load_stackoverflow) 1985-08-05 1985-08-05

Publications (1)

Publication Number Publication Date
US4775042A true US4775042A (en) 1988-10-04

Family

ID=27461482

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/836,507 Expired - Fee Related US4775042A (en) 1985-03-06 1986-03-05 Clutch disc

Country Status (2)

Country Link
US (1) US4775042A (enrdf_load_stackoverflow)
DE (1) DE3607240A1 (enrdf_load_stackoverflow)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4944499A (en) * 1988-02-10 1990-07-31 Kabushiki Kaisha Daikin Seisakusho Damper disk
US5017179A (en) * 1988-06-22 1991-05-21 J.M. Voith Gmbh Flexible coupling with load variable damping
US5049111A (en) * 1988-08-30 1991-09-17 Valeo Torsion damping device having two coaxial parts mounted for relative angular displacement and incorporating a viscous damping device and a friction damping device
US5062517A (en) * 1990-10-09 1991-11-05 General Motors Corporation Tuned damper for a torque converter clutch
US5070974A (en) * 1990-09-19 1991-12-10 Borg-Warner Automotive Transmission & Engine Components Corporation Hydraulic torsional vibration damper
US5083980A (en) * 1988-10-05 1992-01-28 Valeo Viscous torsion damper, particularly for an automotive vehicle
US5097722A (en) * 1989-08-29 1992-03-24 Kabushiki Kaisha Daikin Seisakusho Liquid viscous damper
US5180044A (en) * 1989-12-22 1993-01-19 Kabushiki Kaisha Daikin Seisakusho Liquid viscous damper
US6471593B1 (en) * 1998-05-19 2002-10-29 Voith Turbo Gmbh & Co. Kg Device for absorbing oscillations, especially an oscillation damper
US20060071997A1 (en) * 2004-10-04 2006-04-06 Oce-Technologies B.V. Sheet handling device with sheet support plate and temperature control system
US20120077606A1 (en) * 2010-09-24 2012-03-29 Aisin Seiki Kabushiki Kaisha Torque fluctuation absorber
WO2012150402A1 (fr) * 2011-05-04 2012-11-08 Valeo Embrayages Dispositif d'amortissement de torsion comportant des organes élastiques dont chacun est maintenu individuellement en position par une rondelle de phasage
US9005037B2 (en) 2011-04-28 2015-04-14 Zf Friedrichshafen Ag Rotational vibration damper, particularly for the power train of a vehicle

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63115915A (ja) * 1986-11-03 1988-05-20 ヴィスコドライヴ・ゲゼルシャフト・ミット・ベシュレンクテル・ハフツング クラッチディスク
US5156067A (en) * 1988-04-01 1992-10-20 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device
EP0339805B1 (en) * 1988-04-01 1993-12-15 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device with a damping mechanism utilizing a fluid flow
US5269199A (en) * 1988-04-01 1993-12-14 Toyota Jidosha Kabushiki Kaisha Torional damper type flywheel device
FR2655115B1 (fr) * 1989-11-30 1993-01-22 Valeo Amortisseur de vibrations, notamment pour vehicule automobile.
US5590752A (en) * 1992-10-30 1997-01-07 Kabushiki Kaisha Daikin Seisakusho Clutch disc assembly
DE4337069C2 (de) * 1992-10-30 2001-04-12 Exedy Corp Kupplungsscheibenausbildung

Citations (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE307086C (enrdf_load_stackoverflow) * 1920-09-04
SU233368A1 (enrdf_load_stackoverflow) *
US1455265A (en) * 1923-05-15 Shock absorber
US2124013A (en) * 1936-10-05 1938-07-19 Ira Saks Clutch plate
FR832195A (fr) * 1937-01-27 1938-09-22 Perfectionnements apportés aux amortisseurs hydrauliques d'oscillations
US2337134A (en) * 1940-01-29 1943-12-21 Thelander W Vincent Clutch plate
US2513379A (en) * 1944-09-28 1950-07-04 Dana Corp Friction clutch plate
US2674863A (en) * 1947-12-24 1954-04-13 Dana Corp Friction clutch plate
DE974310C (de) * 1953-10-25 1960-12-22 Kloeckner Humboldt Deutz Ag Hydraulischer geschlossener Drehschwingungsdaempfer, vorzugsweise fuer Brennkraftmaschinen
FR1350917A (fr) * 1963-01-15 1964-01-31 Amortisseur pour voitures
DE2311651A1 (de) * 1973-03-09 1974-09-12 Hemscheidt Maschf Hermann Schwingungsdaempfungseinrichtung
DE2343791A1 (de) * 1973-08-30 1975-03-27 Porsche Ag Hydraulischer daempfer, insbesondere fuer die laufraeder von panzerfahrzeugen
SU574560A1 (ru) * 1976-04-14 1977-09-30 Druzhinin Gavriil F Муфта дружинина г.ф. дл передачи вращени через герметичную перегородку
FR2356847A1 (fr) * 1976-06-30 1978-01-27 Peugeot Dispositif amortisseur perfectionne, notamment pour la suspension d'un moteur
DE2742664A1 (de) * 1977-09-22 1979-03-29 Stromag Maschf Schwingungsdaempfende kupplung
GB2022776A (en) * 1978-06-09 1979-12-19 Daimler Benz Ag Torque Transmission Device
DE3107517A1 (de) * 1980-02-27 1981-12-24 Nissan Motor Co., Ltd., Yokohama, Kanagawa Hydraulisch wirkender stossdaempfer
US4351167A (en) * 1978-11-10 1982-09-28 Voith Getriebe Kg Elastic coupling of disc construction
DE3228738A1 (de) * 1981-07-31 1983-04-07 Sachs Systemtechnik Gmbh, 8720 Schweinfurt Torsionsschwingungsdaempfer, insbesondere fuer die kupplungsscheibe einer kraftfahrzeug-reibscheibenkupplung
US4485906A (en) * 1981-07-31 1984-12-04 Sachs-Systemtechnik Gmbh Torsional vibration damper, particularly for the clutch disk of a motor vehicle friction disk clutch
US4549642A (en) * 1982-02-09 1985-10-29 Valeo Torsion dampers
US4565273A (en) * 1982-08-31 1986-01-21 Kabushiki Kaisha Daikin Seisakusho Damper disk having hydraulic shock absorbers
US4601676A (en) * 1982-09-16 1986-07-22 Kabushiki Kaisha Daikin Seisakusho Damper disc

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB748469A (en) * 1952-11-12 1956-05-02 Applic Mach Motrices An improved hydraulic shock absorber
AT332688B (de) * 1973-09-25 1976-10-11 Geislinger Dr Ing Leonard Drehschwingungsdampfer bzw. elastische kupplung
DE2434053A1 (de) * 1974-07-16 1976-02-05 Conair Stossdaempfer
JPS5934895B2 (ja) * 1980-05-07 1984-08-25 マツダ株式会社 自動車用摩擦クラツチデイスク

Patent Citations (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU233368A1 (enrdf_load_stackoverflow) *
US1455265A (en) * 1923-05-15 Shock absorber
DE307086C (enrdf_load_stackoverflow) * 1920-09-04
US2124013A (en) * 1936-10-05 1938-07-19 Ira Saks Clutch plate
FR832195A (fr) * 1937-01-27 1938-09-22 Perfectionnements apportés aux amortisseurs hydrauliques d'oscillations
US2337134A (en) * 1940-01-29 1943-12-21 Thelander W Vincent Clutch plate
US2513379A (en) * 1944-09-28 1950-07-04 Dana Corp Friction clutch plate
US2674863A (en) * 1947-12-24 1954-04-13 Dana Corp Friction clutch plate
DE974310C (de) * 1953-10-25 1960-12-22 Kloeckner Humboldt Deutz Ag Hydraulischer geschlossener Drehschwingungsdaempfer, vorzugsweise fuer Brennkraftmaschinen
FR1350917A (fr) * 1963-01-15 1964-01-31 Amortisseur pour voitures
DE2311651A1 (de) * 1973-03-09 1974-09-12 Hemscheidt Maschf Hermann Schwingungsdaempfungseinrichtung
DE2343791A1 (de) * 1973-08-30 1975-03-27 Porsche Ag Hydraulischer daempfer, insbesondere fuer die laufraeder von panzerfahrzeugen
SU574560A1 (ru) * 1976-04-14 1977-09-30 Druzhinin Gavriil F Муфта дружинина г.ф. дл передачи вращени через герметичную перегородку
FR2356847A1 (fr) * 1976-06-30 1978-01-27 Peugeot Dispositif amortisseur perfectionne, notamment pour la suspension d'un moteur
DE2742664A1 (de) * 1977-09-22 1979-03-29 Stromag Maschf Schwingungsdaempfende kupplung
GB2022776A (en) * 1978-06-09 1979-12-19 Daimler Benz Ag Torque Transmission Device
US4351167A (en) * 1978-11-10 1982-09-28 Voith Getriebe Kg Elastic coupling of disc construction
DE3107517A1 (de) * 1980-02-27 1981-12-24 Nissan Motor Co., Ltd., Yokohama, Kanagawa Hydraulisch wirkender stossdaempfer
DE3228738A1 (de) * 1981-07-31 1983-04-07 Sachs Systemtechnik Gmbh, 8720 Schweinfurt Torsionsschwingungsdaempfer, insbesondere fuer die kupplungsscheibe einer kraftfahrzeug-reibscheibenkupplung
US4485906A (en) * 1981-07-31 1984-12-04 Sachs-Systemtechnik Gmbh Torsional vibration damper, particularly for the clutch disk of a motor vehicle friction disk clutch
US4549642A (en) * 1982-02-09 1985-10-29 Valeo Torsion dampers
US4565273A (en) * 1982-08-31 1986-01-21 Kabushiki Kaisha Daikin Seisakusho Damper disk having hydraulic shock absorbers
US4601676A (en) * 1982-09-16 1986-07-22 Kabushiki Kaisha Daikin Seisakusho Damper disc

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4944499A (en) * 1988-02-10 1990-07-31 Kabushiki Kaisha Daikin Seisakusho Damper disk
US5017179A (en) * 1988-06-22 1991-05-21 J.M. Voith Gmbh Flexible coupling with load variable damping
US5049111A (en) * 1988-08-30 1991-09-17 Valeo Torsion damping device having two coaxial parts mounted for relative angular displacement and incorporating a viscous damping device and a friction damping device
US5083980A (en) * 1988-10-05 1992-01-28 Valeo Viscous torsion damper, particularly for an automotive vehicle
US5097722A (en) * 1989-08-29 1992-03-24 Kabushiki Kaisha Daikin Seisakusho Liquid viscous damper
US5180044A (en) * 1989-12-22 1993-01-19 Kabushiki Kaisha Daikin Seisakusho Liquid viscous damper
US5070974A (en) * 1990-09-19 1991-12-10 Borg-Warner Automotive Transmission & Engine Components Corporation Hydraulic torsional vibration damper
US5062517A (en) * 1990-10-09 1991-11-05 General Motors Corporation Tuned damper for a torque converter clutch
US6471593B1 (en) * 1998-05-19 2002-10-29 Voith Turbo Gmbh & Co. Kg Device for absorbing oscillations, especially an oscillation damper
US20060071997A1 (en) * 2004-10-04 2006-04-06 Oce-Technologies B.V. Sheet handling device with sheet support plate and temperature control system
US20120077606A1 (en) * 2010-09-24 2012-03-29 Aisin Seiki Kabushiki Kaisha Torque fluctuation absorber
US8523685B2 (en) * 2010-09-24 2013-09-03 Aisin Seiki Kabushiki Kaisha Torque fluctuation absorber
US9005037B2 (en) 2011-04-28 2015-04-14 Zf Friedrichshafen Ag Rotational vibration damper, particularly for the power train of a vehicle
WO2012150402A1 (fr) * 2011-05-04 2012-11-08 Valeo Embrayages Dispositif d'amortissement de torsion comportant des organes élastiques dont chacun est maintenu individuellement en position par une rondelle de phasage
FR2974871A1 (fr) * 2011-05-04 2012-11-09 Valeo Embrayages Dispositif d'amortissement de torsion comportant des organes elastiques dont chacun est maintenu individuellement en position par une rondelle de phasage
US9366312B2 (en) 2011-05-04 2016-06-14 Valeo Embrayages Torsion damping device comprising elastic members held individually in position by phase washer

Also Published As

Publication number Publication date
DE3607240C2 (enrdf_load_stackoverflow) 1991-12-19
DE3607240A1 (de) 1986-09-18

Similar Documents

Publication Publication Date Title
US4775042A (en) Clutch disc
EP0476803B1 (en) Hydraulic torsional vibration damper
US5305858A (en) Rotary shock absorber having vanes with radial flow clearance
JPH09229140A (ja) 粘性ダンパー機構
US5353664A (en) Torsional vibration damping device
JPH0582492B2 (enrdf_load_stackoverflow)
US5573460A (en) Torsional vibration dampening device having multiple dampening force levels with transitional dampening means between multiple dampening force levels
US4555008A (en) Damper disc suitable for automobile clutch
JPS612967A (ja) ねじれ吸収機構
JPH04290636A (ja) トーション制動アセンブリ
US4914799A (en) Method of forming, assembling, and filling a viscous damper
GB2325969A (en) Torsion vibration damper with a friction device
US5123633A (en) Fluid-filled elastic rotational coupling having two fluid chambers on each side of wing members
JPH01220747A (ja) 車両用ねじり減衰装置
KR0140056B1 (ko) 진동 감쇠장치를 구비한 플라이 휘일 어셈블리
EP0364221B1 (en) Viscous damper with means preventing sidewall deflection
US5569086A (en) Viscous fluid torsional vibration dampening device having an elastic slider configured to provide friction dampening
JP2836386B2 (ja) ロックアップクラッチ付き流体伝動装置
US4962838A (en) Viscous damper with low seal drag torque
US5569087A (en) Torsional vibration dampening device having multiple slider mechanisms to provide multiple dampening force levels
JPH0949531A (ja) 粘性抵抗発生機構
JPH04290635A (ja) トーション遮断装置用流体継手
JPH0727174A (ja) 粘性捩じり振動減衰装置
JPH038810Y2 (enrdf_load_stackoverflow)
JPS61189325A (ja) 粘性ダンパ−デイスク

Legal Events

Date Code Title Description
AS Assignment

Owner name: NISSAN MOTOR CO., LTD. NO. 2, TAKARA-CHO, KANAGAWA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:KOHNO, SATOSHI;KIKUCHI, KAZUHIRO;YAMADA, YOUICHIRO;AND OTHERS;REEL/FRAME:004524/0089;SIGNING DATES FROM 19860207 TO 19860212

Owner name: ATSUGI MOTOR PARTS CO., LTD. NO. 1370, ONNA, ATSUG

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:KOHNO, SATOSHI;KIKUCHI, KAZUHIRO;YAMADA, YOUICHIRO;AND OTHERS;REEL/FRAME:004524/0089;SIGNING DATES FROM 19860207 TO 19860212

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
FP Lapsed due to failure to pay maintenance fee

Effective date: 20001004

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362